Dispenser mechanism

ABSTRACT

A MECHANISM FOR AUTOMATICALLY AND MECHANICALLY DISPENSING MEASURED QUANTITIES OF SEMISOLID FOOD PRODUCTS   SUCH AS ICE CREAM OR THE LIKE FROM A REFRIGERATED STORAGE DRUM.

United States Patent [56] References Cited UNITED STATES PATENTS 7/1920 [72] Inventor George A. Tomik Willow Hill Farm, Rte. 2, Peotone, 111. 60468 1 [21] Appl. No. 822,643 22 1 Filed May 7,1969 [45] Patented June 28, 1971 54 DISPENSER MECHANISM 25 Claims, 14 Drawing Figs.

y and mechanicasured quantities of semisolid food ABSTRACT: A mechanism for automaticall cally dispensing m products such as ice cream or the like from a refrigerated storage drum.

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5 n U .mF H W 5 55 11 [It SHEET 1 [1F 8 PATENTED JUN28 1971 Inventor George A. Tomi k WWW Attorney PATENTEU JUN28 I971 SHEET 2 OF 8 '93 Inventor George A Town k Aflorney PATENTEDJuN28|sn 3581478.

I09 I07 I08 Inventor I53 48 George A.Tomik PATENTEDJUN28I97I $587,478

saw u 0F 8 Inventor George A.Tomik Attorney PATENTEU JUN28 I971 SHEET 5 OF 8 PATENTED JUN28 I971 SHEET 6 BF 8 FIG. 7

PATENTED JUN28I971 3581478 SHEET 8 BF 8 FIG. 8

Inventor George A.Tomik H66: By

dispensing soft semisolid materials, and, more particularly, to

a new and improved mechanism for dispensing semisolid food products such as ice cream or the like contained. when in a stored condition, within an elongated, generally cylindrically packing container which is constructed of a plurality of tubular shaped members or sections arranged end-to-end.

U.S. Pat. No. 2,899,915, which issued on Aug. 18, 1959 and of which the present applicant is the inventor, enumerated with particularlity the many problems and difficulties encountered and involved in manually dispensing ice cream in waffletype cones, commonly referred to as ice cream cones, or other receptacles. The dispensing mechanism disclosed in the aforementionedpatent mitigated to a large extent the many shortcomings existing and inherent in the then generally employed hand-scooping method for dispensing measured quantities of ice cream in ice cream cones or the like. Utilization of applicants' patented dispensing mechanism permitted automatic dispensing of uniform, portions of ice cream in a hygenic manner free from contamination and with a minimum amount of effort. Furthermore, there was no assurance that the dispensed balls or scoops of ice cream were of uniform size when the hand-scooping method was employed.

Althoughthe patented dispenser mechanism eliminated the tedious task involved inmanually handling ice cream and thus reduced the time andcost of serving ice cream in ice cream cones or other receptacles as well as the unsanitary characteristics inherent in such handling method,- it was necessary to store the ice cream iri'a'somewhat complicated open bottomed packing container of the kind described in applicants US. Pat. No. 2,717,444 which issued on Sept. 13, I955. Briefly, the container comprises a plurality of tubular shaped members fitted together in telescoping relation as well as a plurality of cutting or severing means in the form of looped flexible cutting elements, each of the cutting elements being disposed in a transverse plane, close to the inner periphery of the normally upper end portion ofeach tubular member. Each severing means requires a section of the flexible loop to be projected outwardly through the wall of the member with which it is associated whereby upon grasping of the projecting section by an element of the related dispensing mechanism, the cutting element is withdrawn through thewall of the tubular member so as to sever the ice cream or other product contained in the tubular member from the next tubular member adjacent thereto. It will be appreciated that extreme care had to be exercised when the container was being filled with a product and processed so as to assure the proper and correct orientation of the cutting elements. Hence, it was found somewhat costly and impractical to form an elongated container made up of such tubular sections and cutting elements. Furthermore, that part of the patented dispensing mechanism responsible for engaging the flexible cutting elements of the packing container involved a complicated driven chain device provided with a plurality of hook members which was prone to malfunction. The operation of the severing mechanism had to be accurately and painstakingly controlled in relation to and synchronized with the other sections of the dispensing mechanism to avoid malfunctioning. Accordingly, it is the prime objective of the present invention to obviate the various shortcomings of'applicants patented dispensing mechanism 'and packing container briefly referred to above without sacrificing the desirable features inherent in and encompassed by such dispensing mechanism and packing container for hygenically dispensing ice cream or other semisolid food products in uniform portions and with a minimum amount of manual effort.

A further objective is to provide a new and improved dispenser mechanism for dispensing measured and uniform quantities of semisolid food products which mechanism has a unique product-severing means incorporated therein.

A still further object is to provide a dispenser mechanism which does not require the use of packing containers for the product of the kind .described in US. Pat. No. 2,717,444 embodying separate cutting means or the like.

The present invention is an improvement of that shown and described in US. Pat. No. 2,899,915 and one of the primary objects of the-invention is to simplify the dispenser mechanism structure and operation of that patent and thereby reduce manufacturing and maintenance costs and insure trouble-free functioning. I

The foregoing and other important objects and desirable features, inherent and encompassed by the invention, together with many of the purposes and uses thereof, will become readily apparent from a reading of the ensuing description in conjunction with the annexed drawings, in which,

FIG. 1, is a perspective view ofa dispensing mechanism embodying the invention; certain lines are broken away and eliminated to better illustrate theinvent'ion;

FIG. 2 is an enlarged front elevational view of the invention, partly broken away and partly in section, illustrating the general arrangement and orientation of certain components thereof during one operational phase of the dispensing mechanism;

' FIG. 3 is a front elevational view of the dispenser mechanism of the present invention, partly in section and partly broken away to better illustrate the invention, illustrating the general orientation and positions of various components and elements of the dispenser mechanism at the commencement ofa dispensing operation cycle;

FIG. 4 is an enlarged front elevational view of the invention, similar to FIG. 3 with the exception that only the components and elements on only one side of the vertical centerline are illustrated and such components and elements are shown in the positions assumed thereby during one operational phase of the dispensing cycle;

FIG. 4A is an enlarged front elevational view, similar to FIG. 4 but showing the orientation of various components and elements during a second operational phase of the dispensing cycle;

FIG. 4B is an enlarged front elevational view showing the same components and elements illustrated in FIG. 4A but as oriented during a third operational phase ofthe dispensing cycle; and

FIG. 4C is an enlarged front elevational view, similar to FIG. 4B and showing the orientation and the relative positions of various components and elements with respect to each other during a fourth operational phase of the dispenser mechanism;

FIG. 5 is a vertical sectional view of the refrigerated container storage means;

FIG. 6 is a fragmentary horizontal sectional view of the storage means shown in FIG. 5;

FIG. 7 is a perspective view of one of the packing containers utilized with the dispenser mechanism of the present invention; FIG. 7A is a view similar to FIG. 7 showing a single container section; and

FIG. 8 is a somewhat diagrammatic view of the electrical components and the electrical circuitry therefor; FIGS. 8A and 8B are similar to FIG. 8, but showing the orientation of certain components during different operational steps of the operating cycle.

Referring to the drawings in detail, wherein like reference characters represent like elements throughout the various views, an ice cream dispenser mechanism embodying the invention is shown in FIG. 5 and is designated in its entirety by reference numeral 10. The dispenser 10 is provided with a suitable stationary base structure 11 (partially shown) supporting a generally cylindrical container-storage housing 12. The housing 12 is formed with spaced inner and outer walls l3, 14, respectively, between which is disposed suitable heat insulation material 15. The top of the housing 12 is closed by a removable cover 16.

Centrally disposed within the housing 12 is a generally vertical standard 17. Extending vertically from the uppermost end of the standard 17 is a stub shaft 18 which has its lowermost end suitably secured to the standard. The housing 12 is also provided with a rotatable perforated, generally cylindrical drum [9. The uppermost end of the drum 19 is provided with a securely fastened end plate 20 to which a bevel gear 21 is rigidly fastened. The stub shaft 18 extends loosely through the end plate 20, as shown in FIG. 5. The drum 19 is supported on the standard 17 for relative rotational movement by means of an antifriction bearing 20'. From the foregoing, it will be appreciated that the drum 19 and bevel gear 21 are capable of rotating with respect to the standard 17 and the housing 12.

A collar 22 is fastened to midsection of the stub shaft 18 and is provided with a bearing 23 for rotatably supporting one end of an indexing shaft 24. The indexing shaft 24 extends radially through the wall of the housing 12 and the end thereof disposed exteriorly of the housing outer wall 14 is provided with a suitable operating handle (not shown) for manually rotating the indexing. shaft 24. As shown in FIG. 5, the indexing shaft 24 is journaled in a bearing 25 provided in the wall of the housing 12 and a bevel gear sector 26 is'keyed or otherwise suitably secured to a section of the shaft 24 intermediate its ends. During each complete revolution of the indexing shaft 24, the bevel gear sector 26 is brought into and out of meshing engagement with the bevel gear 21. In this manner, the bevel gear 21 and thus the drum 19 are intermittantly rotated a predetermined distance during each complete revolution ofthe indexing shaft 24.

Stationary refrigerant coils 27 are disposed between the drum l9 and the standard 17. The refrigerant coils 27 are operatively connected to a conventional refrigerating compressor unit (not shown). The bottom of the housing 12 is partially defined by a generally flat and smooth, annular floor 28 radially disposed between the inner wall 13 of the housing 12 and the drum 19.

The floor 28 is adapted to support a plurality of circum ferentially spaced, vertically disposed, open bottom, multisectioned packing containers, each being designated in its entirety by reference numeral 29. Referring to FIG. 7, it will be noted that each packing container 29 is comprised ofa plurality of separate sections 30 made of plastic material or other material having like physical characteristics. Each container section 39 includes a generally cylindrical body 31 having an enlarged annular portion 32 at one end only ofa slightly larger diameter. The annular end portion 32 serves as a socket for receiving the end portion 33 opposite the enlarged annular portion 32 of an adjacent container section 30. The free end of the annular portion 32 is provided with an integrally formed, radially extending flange 34. The periphery of the flange 34 has a notch 35 formed therethrough, the purpose of which will be pointed out presently. The separable container sections 30 are arranged end-to-end and telescoped together to form the longtubularly shaped packing container 29. It will be noted that the container sections 30 are assembled together with their respective notches 35 in longitudinal alignment as shown in FIG. 7. In use, a plurality of unfilled container sections 30 are assembled in the aforestated manner to form a packing container 29 of any desirable height and thereafter, a commodity product in liquid or semiliquid condition is poured into one end of the packing container, after closing or sealing the opposite end thereof, to fill the same. The commodity product is then refrigerated to convert the liquid or semiliquid substance to a solid or semisolid condition. The packing container 29 is broadly similar to the container described and claimed in U.S. Pat. No. 2,717,444 except that its construction has been modified to eliminate the necessity of providing each container section 30 with its own flexible cutting means. Accordingly, the processing of packing container 29, including the assembly of the container sections 30 and the filling of the assembled packing container, has been greatly simplified. While the separable container sections 30 and the bodies 31 thereof have been referred to hereinbefore and will be referred to hereinafter in the specification and claims as being generally cylindrical in shape, it is to be understood that the body 31 of each container section 30 is, preferably, slightly tapered by having its normally uppermost internal diameter slightly larger than the internal diameter of the opposite or lowermost end. By forming the generally cylindrical body 31 of each container section 30 with a slight taper, stripping or separation of each container section 30 from the packing container 29 and the mass of material contained in the body 31 is facilitated, as will be pointed out hereinafter in detail.

Referring specifically to FIGS. 5 and 6, a plurality of processed packing containers 29 filled with ice cream or the like, are placed in the housing 12. The packing containers 29 are supported on the annular floor 28. It will be noted that the radial spacing between the drum 19 and the inner housing wall 13 is only slightly larger than the diameter of a container section flange 34. Thus, the inner housing wall 13 and the drum 19 serve to guide the packing containers 29 as they are being moved in conjunction with rotation of the drum 19 for a purpose which will be pointed out hereinafter. The structure for imparting movement of the packing containers 29 upon rotation of the drum 19 includes a plurality ofvertically disposed, elongated pusher bars 36. Each pusher bar 36 is associated with a respective one of the packing container 29 and is formed so that a center portion-37 in horizontal cross section, is substantially U-shaped and conforming to the outline of the notches 35. The center portion 37 is adapted to be positioned within the vertically aligned notches 35 of the container sections 30 of a processed and assembled packing container 29. The pusher bar 36 is also formed with oppositely extending, arcuate extension 38. Each extension 38 has a radius ofcurvature substantially the same as the radius of curvature of the outer periphery of a container section flange 34. As best shown in FIG. 6, the extension 38 of each pusher bar 36 are adapted to abut portions of the flange 34 disposed on each side of the notch 35 of each container section 30 of the assembled packing container 29.

Each pusher bar 36 is operatively connected to the drum 19 by means of three vertically spaced, generally radially extending arms 39. The arms 39 have one end rigidly fastened to the drum 19 by any suitable means. A pivot pin 40 is carried by the opposite end portion of the arm 39 to which is attached a pair of vertically spaced, horizontal tabs 41 struck from the pusher bar center portion 37. From the foregoing, it will be appreciated that each pusher bar 36 is capable of swinging about a respective vertical axis with respect to its supporting arms 39 and the drum 19.

In order to dispense the ice cream or other food product contained in the individual, separable container sections 30 of a packing container 29, it is necessary that such packing container 29 be properly positioned in relation to the housing 12. An ejection apparatus, designated generally by reference character 42, includes a packing container receiving chute 43 which is radially offset outwardly from the annular floor 28 and is partially defined by a substantially arcuate wall section 44 connected to the inner wall 13 over an opening therein and serving as a continuation of the inner wall 13. The radius of curvature of the arcuate wall section 44 is substantially the same as the radius of curvatureof the outer periphery of a container section flange 34. It will also be noted that the wall section 44 extends arcuately approximately In use, the cylindrical, refrigerated housing 12 is first charged or loaded with one or more packing container 29, each filled with, as an example with ice cream. Each packing container 29 is positioned within the housing 12 so that the center portion 37 of a respective pusher bar 36 is disposed within the vertically aligned notches 35 of the separable container sections 30 thereof. It will be appreciated that when the pusher bar 36 and the packing container 29 are oriented with respect to each other in this manner, the arcuate extensions 38 are also in abutting engagement with the container section flanges 34. From the foregoing, it is believed clear that upon rotation of the drum in a counterclockwise direction, as viewed in FIG. 6, the packing containers 29 are simultaneously propelled and slide on the floor 28. As is apparent from viewing FIG. 6, the pivotal connection between the pusher bars 36 and the arms 39 causes the pusher bars 36 to be selfaligning so that the propelling force exerted by the arms 39 on the packing containers 29 is always in the proper direction to avoid tilting or canting of the packing containers 29. Means are provided for guiding the packing containers 29 to the chute 43 and such means includes two radially spaced sets of baffles 45, 450. Each of the baffle sets 45, 4511 includes at least one arcuately shaped baffle 46, 47, respectively. Baffle 46, of which there are preferrably two in vertical alignment, although only one is shown in FIG. 6, is integrally formed with the inner wall 13 and is curved so as to extend radially inwardly from the inner wall 13 at one end of the chute 43 and project over the floor 28. The baffle 47 of the other baffle set 45 is securely fastened to the floor 28 and has substantially the same radius of curvature as the baffles 46. The baffle 47 extends from the drum l9 and is in arcuate alignment with the baffles 46. The radial spacing between the baffles 46 and the baffle 47 is considerably less than the diameter of the packing containers 29 but large enough to accommodate passage of a pusher bar 36 therebetween.

Assuming that the chute 43 is empty and it is desired to dispose a packing container 29 therein so as to be properly positioned to be acted upon by the ejection apparatus 42, the operator merelygrasps the operating handle (not shown) and rotates the shaft 24 one complete revolution. Rotation of the shaft 24 one revolution, in turn, causes the drum 19 and, hence, the packing containers 29 within the refrigerated housing 12 to move a predetermined arcuate distance. The pitch diameter of the bevel gear sector 26 and the number of teeth provided thereon in relation to the pitch diameter of the bevel gear 21 is chosen so that during each complete revolution of the shaft 24, the packing containers 29 are moved circumferentially a distance approximately equal to the maximum diameter of a packing container 29. As an example, if the housing 12 was of sufficient size to accommodate packing containers 29 including one packing container 29 disposed in the chute 43, then the pitch diameter and number of teeth chosen for the bevel gear sector 26 would result in the packing containers 29 moving approximately 36 circumferentially along the annular floor 28. From the foregoing, it is believed obvious that during rotation of the shaft 24 the packing container 29 disposed at the station adjacent to and clockwise from the chute 43, as viewed in FIG. 6, not only moves circumferentially in a counterclockwise direction but also is simultaneously moved radially outwardly so as to be positioned within the chute 43 upon completion of the one revolution of the shaft 24. The outward movement of the packing container 29 is effected by the joint action of the camming effect provided by the baffles 46 and 47 and the radially outwardly directed force component exerted by the pusher bar 36 associated therewith it will be noted that as the packing container 29 is moved toward its proper position completely within the chute 43, the pusher bar 36 pivots in a clockwise direction, as viewed in FIG. 6, with respect to its supporting arms 39 and by the time movement of the drum l9 ceases and the packing container 29 is disposed within the chute 43, the center portion 37 of the pusher bar 36 is projecting radially outwardly. Further pivotal movement of the pusher bar 36 with respect to the supporting arms 39 in clockwise direction when the pusher bar 36 is in this position is prevented by stop means in the form of abutments 48 provided on the arms 39 adjacent the pivot pins 40. The abutments 48 engage one of of the curved extensions 38 of the pusher bar 36 to limit relative pivotal movement ofthe pusher bar 36 in one direction. Thus, when the pusher bar 36 is in abutting engagement with the abutments 48 and is stationary it also defines a part of the chute 43 and the interaction ofthe center portion 37 with the notches 35 and the interengagement ofthe extensions with the outer periphery portions of the container section flanges 34 serve to properly guide and feed the packing container 29 to the ejection apparatus 42. it is to be understood that power means in the form of an electric motor or the like could be cmployed for rotating the shaft 24 one complete revolution to index the packing containers 29 one station without departing from the spirit and scope of the invention.

The ejection apparatus 42 includes a supporting frame 49 which is adapted to be detachably connected to the housing outer wall 14 by means which-will be pointed out hereinafter. The base structure 11 supports the refrigerated-packing container storage housing 12. The means provided for removably securing the frame 49 to the outer wall of the housing insure the correct positioning of the ejection apparatus 42 in relation to the chute 43 so that it will operate properly. While the details of the particular means utilized for securing the ejection apparatus 42 to the housing 12 will be described hereinafter, it is to be understood at this point that the ejection apparatus 42, in toto, may be readily assembled on or disassembled from the housing 12 quickly and with a minimum amount ofeffort.

' As shown in FIG. 6, cavities 50 are formed in the insulating material 15 radially outwardly of the housing inner wall 13. The cavities 50 are defined by a sheet metal casing 51 and such cavities open into the bottom of the housing outer wall 14. The cavities 50 accommodate various parts and components of the ejection apparatus 42, as will be pointed out hereinafter, and the casing 51 serves to separate such parts and components from the interior of the housing 12 and the heat insulating material 15.

The ejection apparatus 42, as shown in FIG. 1, is comprised of various elements and components mounted on the frame 49 which are adapted to dispense the ice cream or other food product contained in the lowermost container section 30 of the packing container 29 disposed in the chute 43 during each cycle of operation and such dispensing is done in a sequential manner. Briefly, such sequence involves moving of the lowermost container section 30 from the interior of the housing 12, forcibly stripping and ejecting the lowermost container section 30 from the packing container 29, and exposing the ice cream formerly container with the ejected container section, severing the exposed ice cream from the packing container 29, and then repositioning the packing container 29 in the interior of the housing 12. The supporting frame 49 is provided with suitable bearings for rotatably supporting a horizontally extending main drive shaft 52 as well as other shafts which will be described hereinafter. A relatively small gear segment 53 is rigidly fastened to the shaft 52 adjacent one end thereof. A main drive gear segment 54 is keyed or otherwise rigidly secured to the shaft 52 intermediate its ends. The main drive shaft 52 also carries a bevel gear segment 55 which is nonrotat'ively connected thereto. The ejector apparatus 42'also includes a shaft 56, vertically spaced and parallel to the shaft 52, which has a pair of spaced gears 57 and 58 rigidly connected thereto. The gear 58 is sandwiched between and free to rotate with respect to a pair of spaced and parallel side plates 59, 60 of a generally vertically disposed gear and rack housing 61,

shown in FIG. 2. The gear and rack housing 61 is rigidly.

secured to the supporting frame 49 and is thus stationary. The

ejector apparatus 42 further includes a shaft 62 horizontally spaced from and parallel to the shaft 56. The shaft 62 nonrotatably supports a pair of gears 63, 64 which correspond in size, shape and type to the gears 57,58, respectively. Gear 64, like gear 58, is interposed between and free to rotate with respect to the spaced and parallel plates 65, 66 of a second.

and 73 rigidly secured at respective at respective opposite ends thereof. The ejector apparatus 42 further includes a pair of horizontally spaced and parallel shafts 74, 75 which have longitudinal axes extending perpendicular to the longitudinal axis ol'the main drive shaft 52. The shaft 74 has a bevel pinion gear 76 rigidly secured to one end thereof which is meshable I with the bevel gear segment 55 secured to the main drive shaft 52. A flap, designated generally by reference character 77, has one edge portion rigidly secured to a midsection of the shaft 74. The end of the shaft 74 opposite the bevel pinion gear 76 is provided with a rigidly mounted bellcrank 78. The shaft 75 also has a flap 79 secured thereto which is a mirror image of the flap 77. The end of the shaft 75 in horizontal alignment with the bellcrank 78 has a bellcrank 80 rigidly fastened thereto. As clearly shown in FIG. 1, the bellcranks 78 and 80, while of the same length, are angularly oriented l80 out of phase with respect to each other. A connecting rod or the like 81 extends between and is pivotally connected to the bellcranks 78 and 80. It will be appreciated that upon rocking of the shaft 74 in one direction, the shaft 75 will rock the same amount in unison with the shaft 74 but in an opposite direction.

The main drive gear segment 54 is intermittently meshable with the pinion gear 57 secured to the shaft 56 and the pinion gear 58 keyed to the opposite end of the shaft 56 is in mesh with an elongated rack 82 mounted in the gear and rack housing 61, shown in FIG. 2 for vertical relative sliding movement. In addition to the intermittent meshing engagement of the pinion gear 57 with the main drive gear segment 54, the pinion gear 57 also meshes continually with an idler gear 83 which, in turn, meshes with an idler gear 84. The idler gears 83, 84 are rotatably mounted on stubshafts 85, 86, respectively, which extend through the supporting frame 49 and are threaded into nuts welded to the interior surface of the outer wall 14 of the housing 12. The stub shafts 85, 86 and the nuts constitute the quick detachable means for securing the supporting frame 49 and, hence, the entire ejection apparatus 42 to the base structure 11 and the housing 12. The idler gear 84 is in meshing engagement with the pinion gear 63 keyed to one end of the shaft 62. The pinion gear 64, in turn is in meshing engagement with an elongated rack 87 mounted for vertical sliding movement in the gear and rack housing 67.

The main drive shaft 52 is rotated by means of a reversible electric motor 88 which is supported on the frame 49 and is drivingly coupled to an elongated hub portion of the pinion gear 53. The direction ofrotation of the motor 88 is controlled by a reversing toggle switch 89 which is mounted on the stationary frame 49. Energization of the motor 88 is controlled by a main drive motor switch 90 and a starter switch 91, shown diagrammatically in FIG. 8. The operation and function of the switches 89, 90 and 91 during a complete operational cycle of the ejector apparatus 42 will be pointed out hereinafter in detail.

From the foregoing, it will be appreciated that counterclockwise rotation, as viewed in FIG. 1, of the main drive gear segment 54 from the position illustrated in FIG. 1 causes the bevel gear segment 55 to also rotate counterclockwise which, in turn, effects counterclockwise rotation of the bevel pinion gear 76 rigidly fastened on the common shaft 74 with the flap 77 and bellcrank 78. Inasmuch as the shaft 75 is interconnected to the shaft 74 as pointed out hereinbefore such counterclockwise rotation of the shaft 74 is effected simultaneously with clockwise rotation of the shaft 75 and the flap 79 rigidly fastened thereto. The flaps 77 and 79 are positioned at the open bottom of the packing container receiving chute 43 and when in the horizontally disposed position, as illustrated in FIG. 1, they are effective to close the exterior opening into the chute 43 and thus the refrigerated interior ofthe storage housing 12. However, when the shafts 74 and 75 are rocked in the manner pointed out hereinbefore, the flaps 77 and 79 swing downwardly to thereby uncover the exterior bottom opening of the chute 43.

counterclockwise rotation of the main drive gear segment 54 also effects clockwise rotation ofthe pinion gear 57 and the shaft 56 since the pinion gear 63 and shaft 62 are operatively connected to the shaft 56 through the intermediary ofthe idler gears 83 and 84, as pointed out hereinbefore, pinion gear 63 and shaft 62 will simultaneously rotate in a counterclockwise direction, as viewed in FIG. I and as indicated by the arrows. Inasmuch as the pinion gears 58 and 64 are keyed to the shafts 56 and 62, respectively, such counterclockwise rotation ofthe main drive gear segment 54 also effects vertical downward movement of the racks 82 and 87.

Referring to FIG. 3 the structure and construction of the gear and rack housings 61 and 67 will now be described in detail. However, since the gear and rack housings 61 and 67 are substantially mirror images of each other, reference will only be made to gear and rack housing 61 although it is to be understood that the structure and construction of the gear and rack housing 67 are substantially the same as the structure and construction of the gear and rack housing 61. The spaced and vertically disposed plates 59 and 60 of the gear and rack housing 61 have a somewhat L-shape in front elevation, with the shorter leg portion 92 of each plate 59 and 60 extending horizontally toward the chute 43 and the longer leg portions 93 extending vertically. The uppermost end portion of a rack bearing member 94 is rigidly connected to and between the leg portions 92 of the plates 59 and 60. The rack bearing member 94, which has a generally rectangular shape in horizontal cross section, is secured to and depends vertically from the leg portions 92 and is provided with a flat, straight edge surface 95 which is horizontally spaced from and parallel to a vertical plane containing a flat straight edge surface 96 of each of the vertical leg portions 93 of the plates 59 and 60. One of the purposes of the straight edge surface 95 is to provide a bearing surface for the edge surface 97 of the rack 82 opposite the edge upon which the gear teeth 98 are formed so as to facilitate vertical sliding movement of the rack 82. It will also be noted that the rack 82 extends between the horizontally spaced leg portions 92. The horizontal spacing of the leg portions 92 is sufficient to accommodate the rack 82 therebetween and hence, assist in preventing dislodgement of the rack edge surface 97 from the bearing surface 95 of the rack bearing member 94. A dog, designated generally be reference numeral 99, is pivotally connected to the rack 82 intermediate its ends. The dog 99 is generally U-shaped in plan. The bight portion thereof is capable of functioning as a container section flange-engaging Iip 100 in a manner which will be pointed out hereinafter in detail. When the rack 82 is in its uppermost position, as illustrated in FIG. 3, the rack bearing member 94 extends between the lip 100 and the rack edge surface 97 as well as between horizontally spaced leg portions 101 of the dog 99. The dog is pivotally connected to the rack 82 by means of a pin 102 extending horizontally through the spaced leg portions 101, which closely embrace the rack 82. The free end portions I03 extend horizontally beyond the flat wedge surfaces 96 of the vertical leg portion 93 of the plates 59 and 60 so as to overlap the plates 59 and 60 when in the position shown in FIG. 3. The inwardly facing surface of each of the overlapping end portions 103 sliding engages the outwardly facing surface of a respective one of the leg portions 93. Inasmuch as the horizontal spacing between the inwardly facing surfaces of the overlapping end portion 103 is greater than the horizontal spacing between the inwardly facing surfaces of the leg portion 101 generally, each leg portion 101 is formed with a shoulder 104. Each shoulder 104 defines the limit of a respective overlapping end portion 103 and is adapted to slidingly engage the flat edge surface 96 of the vertical leg portion 93 of a respective plate 59, 60. From the foregoing, it will be appreciated that whenever the shoulders 104 are in abutting engagement with the flat edge surfaces 96, the dog 99 is maintained in its horizontally disposed position as shown in FIG. 3. However, when the rack 82 and dog 99 are moved vertically downwardly from the position shown in FIG. 3 to a position wherein the shoulders 104 are below the lowermost ends (indicated by reference numeral 105) of the flat edge surface 96 and are no longer in engagement therewith, as shown in FIG. 4, the dog 99 is free to pivot about the axis of the pivot pin 102. It will be noted, that when the dog 99 is in its tilted position, as shown in FIG. 4, the lip 100 is disposed radially outwardly of the outer peripheral edges 106 of the section flanges 34 of the packing container 29 disposed within the chute 43. However, when the dogs 99 are in their horizontal positions, the lip 100 extend radially into the chute 43 and when in this position are capable of engaging the underside of the flange 34 of a respective container section 30 so as to support the packing container 29 disposed within the chute 43, as illustrated in FIG. 3.

Referring to FIG. 3, it will be noted that a sliding stop member, designated generally be reference numeral 107 is provided vertically below each gear and rack housing 61, 67. Inasmuch as both sliding stop members 107 are constructed exactly alike and operate in the same manner, only the construction and operation of the sliding stop member 107 disposed on the left-hand side as viewed in FIG. 3 will be described in detail. The stop member 107, which has a generally rectangular "configuration in vertical end section, is supported for horizontal sliding movement by means which includes a generally U-shaped bearing channel 108 which is integrally formed with the supporting frame 49. The means for slidably supporting the stop member 107 also includes a generally L-shaped plate 109 which is interposed between the bottom of the gear and rack housing plates 59 and'60 and the top of the bearing member 108. The short leg portion 110 of the L-shaped plate 109 is vertically disposed and the inwardly facing surface lll 'thereof lies substantially in the vertical plane containing the top surfaces 112 of the teeth of the rack 82. The leg portion 110 serves as a backrest for the rack 82 in a manner that will be pointed out hereinafter. The horizontally disposed leg portion 113 of the L-shaped plate 109 is provided with a central, elongated slot 114 therethrough. A pin 115, having one end threaded into the sliding stop member 107, extends vertically through the slot 114. One end of a helically wound tension spring 116 is connected to the pin 115 and the opposite end of the spring 116 is fastened to a stationary pin 117 fixedly connected to the bearing member 108. The stop member 107 is provided with an elongated slot 117' therethrough which has one end opening in the outermost end of the stop member 107. The slot 117 accommodates the stationary pin 117 therethrough. When pin 117 is in engagement with the surface of the stop member 107 defining the bottom or closed end of, the slot 117, further sliding movement horizontally outwardly is prevented. From the foregoing it'will be appreciated that the tension spring 116 yieldably urges the stop member 107 to the left, as viewed in FIG. 3, causing the pin 115 to be disposed at one end of the slot 114. When the pin 115 is in the position illustrated in FIG. 3 closely adjacent to the wall surface defining one end of the slot 1l4,the stop member 107 is in its fully retracted position since further movement of the stop member 107 to the'left is prevented by the pin 117 cominginto abutting engagement with the surface defining the bottom of the slot 117'. The inwardmost end of the stop member 107 is provided with a cam'follower in the form of a roller 118. The roller 118 is capable of rotating about a horizontally extending axis which is horizontally spaced inwardly of the surface 111 of the backrest 110 and vertically spaced above the stop member 107. It will be noted that when the stop member 107 is in its fully retracted position, as illustrated in FIG. 3, the horizontal spacing'between the inwardly facing surface 111 of the backrest 110 and the outer peripheral surface of the roller 118 is considerably smaller than the width-of the rack 82 measured horizontally from the straight edge surface 97 to the vertical plane containing the top surfaces 112 of the rack teeth. It will also be noted that the lower end portion 119 of rack 82 is substantially wedge-shaped in configuration and is provided with cam surface 120 inclined with respect to the rack vertical straight edge surface 97. Thus, it will be appreciated that as the rack 82 moves vertically downwardly from the position shown in FIG. 3 to the position shown in FIG. 4, the lowermost tip of the wedge-shaped end portion 119 first enters the spacebetween the backrest 110 and the roller'118 and as the rack 82 continues in its vertical downward movement, the cam surface 120 engages the roller 118 to force the stop member 107 horizontally to the right against the resilient action of the spring 116 to its fully extended position. Upon withdrawal of the wedge-shaped end portion 119 of the rack 82 from engagement with the roller 118, the spring 116 is effective to return the stop member'107 to its fully retracted position. The stop member 107 is provided with a suitable opening 121 therethrough to accommodate the wedge-shaped end portion 119 of the rack 42 during the ahovedescribed movement of the rack 82.

The innermost end of the stop member 107 is formed with an elongated slot 122 therethrough. The slot opens into the innermost end face 123 of the stop member 107 and the opposite end or bottom of the slot 122 is defined by flat surface 124 having a central recess 125 formed therein. The recess 1'25 serves as a pocket for receiving and confining one end ofa helically wound compression spring 126 which has its opposite end operatively engaging a curved surface 127 of an intermediate portion ofa substantially L-shaped pawl 128.

The intermediate portion of the pawl 128 carries a pivot pin 129 which has end portions projecting in respective opposite directions therefrom. The pawl 128 is disposed within slot 122 and each projecting end portion of the pin 129 is adapted to be slidingly and rotatably received in a respective elongated horizontal slot 130 formed through each leg 131 of a pair of spaced legs of the stop member 107 which legs 131 are partially defined by the slot 122. The spring 126 yieldable urges the pawl 128 inwardly to an extended position wherein each of the projecting end portions of the pin 129 is disposed at the innermost end of a respective slot 130, as shown in FIG. 3. The pawl 128 is horizontally slidable with respect to the stop member 107 between the extended position and a retracted position, illustrated inFlG. 4A, wherein the spring 126 is compressed to its maximum extent. The pawl 128 is also capable I of pivoting approximately 90 with respect to the stop member 107. In a first uncocked condition of the pawl 128, a generally flat'surface 132 of one of the legs 133 of the pawl 128 is substantially horizontally disposed, as shown in FIG. 4, and in a second cocked condition of the pawl 128, a generallyfiat surface 134 of the other pawl leg 135 is substantially horizontally disposed, as illustrated in FIG. 4A. It will be noted that the pawl leg 133 is substantially rectangularly shaped and the pawl leg 135 is substantially triangularly shaped in front elevation. It will also be appreciated that the surface 134 of the pawl leg 135 lies substantially in the same horizontal plane as the top or uppermost surface of the stop member 107 when the pawl 128 is in its cocked condition and such cocked condition of the pawl 128 is established when a flat surface 136 of the pawl leg 133, parallel to the surface 132, abuts an inclined surface 137 formed at the innermost end of the horizontal bight portion of the U-shaped bearing channel 108. It will also be appreciated that the pawl 128 is also in its extended position whenever it is in its cocked condition. Thus, when the pawl leg surface 136 is in engagement with the stationary bearing member inclined end surface 137, further pivotal movement of the pawl 128 in a clockwise direction from the cocked position shown in FIG. 4A is prevented. It will also be appreciated that when pawl 128 is in its cocked condition and the stop member 107 is in its extended position, as illustrated in FIG. 4A, the tip 138 of the pawl leg 135 and the innermost end face 123 of the stop member 107 lie closely adjacent to each other. Preferably, the tip 138 and the innermost end face 123 are formed so as to be curved when viewed in plan and when the pawl 128 is cocked and the stop member is fully extended, they lie substantially in a circle having a radius slightly larger than the radius of curvature of the outer peripheral surface of the enlarged end 32 ofa packing container section 30. The operation of the sliding stop member 107 will be pointed out hereinafter in detail. However, it is to be understood that when the stop member 107 is being moved from its retracted position toward its extended position as sequentially illustrated in FIGS. 3, 4 and 4A, by downward movement of the rack 82 from the position shown in FIG. 3 to the position shown in FIG. 4A, the pawl 128, although still in its retracted position and uncocked condition, is also moved inwardly sufficiently so that the horizontally disposed fiat surface 132 of the pawl leg 133 is disposed in the path of the flange 34 of the lowermost section 30 of the packing container 29, as illustrated in FIG. 3, as the packing container 29 descends in the chute 43 during operation of the dispenser 10. The pawl 128 is then engaged by the flange 34 and caused to he pivoted to its cocked condition. Inasmuch as the pawl 128 is prevented from pivoting clockwise beyond its cocked position, as pointed out hereinbefore, and since the stop member 107 is approaching its fully extended position both the flat surface 134 adjacent the tip 138 of the pawl 128 and the horizontally disposed uppermost surface 139 of the stop member 107 adjacent to the innermost end face 123 thereof which is substantially flush with the pawl surface 134 are adapted to engage the flange 34 of the second section 30 from the bottom asv iewed in FIG. 4A. In this manner, further downward movement of the packing container 29 is prevented and the packing container 29 is firmly supported.

Referring to FIGS. 1 and 2, the ejector apparatus 42 further includes a vertically disposed rack 140 which is suitably supported for vertical sliding movement 'by bearing means, designated generally by reference character 141. The rack 140 is adapted to-intermittently mesh with the small gear segment 53 keyed to the main drive shaft 52. The rack 140 is also in meshing engagement --with the pinion gear 69, which, in turn, is in meshing engagement with an idler gear segment 142 which is rotatably supported on a stub shaft 143 spaced and parallel to a stub shaft 145. An idler gear segment 144 is in meshing engagement with pinion gear 73 keyed to the shaft 71. From the foregoing, it will be appreciated that upon movement of the rack 140 vertically downwardly when the gear segment 53 meshes with the same as it rotates counterclockwise, as viewed in FIG. 1, pinion gear 70 and pinion gear 73 will simultaneously rotate counterclockwise and clockwise, respectively. I 1

Suitably supported in a bracket 146 for horizontal sliding movement is rack 147; The rack 147 is in meshing engagement with the pinion gear70 secured to shaft 68. In a similar manner, a bracket 148 slidably supports a rack 149 which, in turn, is drivingly connected to the pinion gear 73 keyed to the shaft 71. The ejector apparatus 42 includes a pair of generally semicylindrical heater shells 150, 151. The heater shell 150 is pivotally connected to the innermost end of the rack 147 and, in a similar manner, the heater shell 151 is pivotally connected to the innermost end of the rack 149. By pivotally connecting the heater shells 150, 151 to the racks 147, 149, respectively, the heater shells are, in effect, self-aligning and are capable of firmly embracing orenveloping the lowermost container section 30 when the packing container 29 is disposed as shown in FIG. 4A. A pair of helically wound tension springs 152, 153 also form part ofthe ejector apparatus 42. The spring 152 has one end attached to the rack 147 and the other end to support bracket 146 and the other spring 153 is operatively connected between the bracket 148 and the rack 149. The springs I52, 153 serve as means for returning the heater shells 150, 151 to their retracted inoperative positions. From the foregoing, it will be appreciated that counterclockwise rotation of the gear segment 53 when in mesh with the rack 140 will simultaneously effect horizontal sliding movement of the racks 147, 149 and the heater shells 150, 151, respectively carried thereby, inwardly toward each against the biasing action of the return springs 152, 153. At the moment ofdisengagement of the gear segment 53 from the rack 140 as the main drive gear segment 54 simultaneously rotates in a counterclockwise direction, as viewed in FIG. 1, the heater shells 150, 151 will have been moved inwardly toward the center and into firm abutting engagement with the cylindrical body 31 of the lowermost packing container section 30 and against the resilient action of the return springs 152, 153. It is to be understood that the em tire packing container 29 is being supported by the sliding stop members 107 with the lowermost container section 30 being disposed as shown'in FIG; 4A at this time.

Latch means, designated generally by reference character 154, are provided for maintaining the rack 140 in its lowermost position which corresponds to the container section-engaging position of the heater shells 150, 151 for a predetermined period of time after the gear segment 53 moves out of meshing engagement with the rack 140. The heater shells 150, 151 have electrical resistance elements 155 (partially shown) imbedded therein whichare supplied with electric current at least during the aforementioned period time. The heat generated by the electric current passing through the relatively high resistance elements 155 is transmitted to the cylindrical body 31 of the lowermost packing container section 30. The transmitted heat causes the material within and adjacent the cylindrical body 31 to soften or melt so that adherence of the material to the body 31 of the section 30 is lost. The latch means 154 includes a plunger 156 slidably supported in a bracket 157. The plunger 156 has a relatively hard tip portion 158 which has a generally rectangular configuration in vertical section. A helically wound compression spring 159 is employed for yieldably urging the plunger 156 inwardly or to the right, as viewed in FIG. 2. Except during the aforementioned predetermined period of time during which the lowermost container section 30 is being heated, the lowermost edge 160 of the tip portion end face 161 is in sliding engagement with the outer or cam surface 162 of a cam 163 rigidly secured to the main drive shaft 52 intermediate the main drive gear segment 54 and the pinion gear segment 53. It will be noted that when the lowermost edge 160 is in engagement with the cam surface 162, as illustrated in FIG. 2, the tip portion end face 161 lies substantially in the vertical plane containing the vertical edge 164 of the rack opposite the teeth thereof. The cam 163 and thus the cam surface 162 thereof are angularly oriented with respect to the pinion gear segment 53 on the main drive shaft 52 in such a manner that at the point in the operating cycle when the gear segment 53 moves out of meshing engagement with the rack 140, the uppermost end165 of the rack 140 lies substantially in or slightly below a horizontal plane containing the lowermost edge of the tip portion end face 161 and the lowermost edge 160 moves out ofsliding engagement with the cam surface 162, As a result, the plunger spring 159 is effective to force the plunger 156 inwardly to the right, as viewed in FIG. 2, causing the flat underside of the tip portion 158 to overlie and abut the uppermost end of the rack 140. Thus, it will be appreciated that the rack 140 is maintained in its lowermost position corresponding to the container section-engaging position of the heater shells 150, 151 against the biasing action of the return springs 152, 153 even though the gear segment 53 is out of meshing engagement with the rack 140. The rack 140 remains, in effect, locked in its lowermost position until the leading edge of the cam 163 which continues to rotate counterclockwise, as viewed in FIG. 2, engages the lowermost edge 160 of the plunger tip portion 158 to force the plunger 156 outwardly or to the left and tip portion end face 161 to the position shown in FIG. 2. Once the plunger tip portion 158 is moved out of engagement with the rack end 165, the resilient action of the springs 152 and 153 will cause the rack 140 to move to its fully raised position and simultaneously return the heater shells 150, 151 to their fully disengaged positions, as shown in FIG. 2.

A pair of fingers 166, 167, shown in FIG. 3, are employed for stripping the lowermost container section 30 from the ice cream or contents thereof following the container section heating step described above of an operational cycle. The fingers 166, 167 are substantially duplicates of each other. The finger 166 has a midportion pivotally connected to the rack 82 at a point vertically spaced below the dog 99. In a similar manner, the finger 167 is pivotally connected to the rack 87. Each finger 166, 167 is formed with a generally rectangular section 168 extending generally upwardly from the pivotal axis thereof and an elongated tapered section 169 extending generally downwardly from the pivotal axis. The lowermost end of each tapered section 169 is provided with an enlarged arcuately shaped flange-engaging lip 170. The width of the generally rectangular section 168 is substantially the same as the width of the rack 82 or 87. It will also be noted that the longitudinal axis of the rectangular section 168 and the tapered section 169 of each finger 166, 167 are angularly oriented with respect to each other more than 90 but less than I80". Thus, when the fingers 166, 167 are each positioned so that the longitudinal axis of its rectangular section 168 extends vertically as shown in FIG. 4A, the longitudinal axis of the tapered section 169 extends downwardly and inwardly from the pivotal axis thereof and, conversely, when the longitudinal axis of its tapered section 169 is vertically disposed, as shown in FIG. 3, the rectangular section 168 is inclined upwardly and inwardly from the pivotal axis thereof. It is also to be understood that when the fingers I66 and 167 are handing freely, they assume inoperative positions, as illustrated in FIG. 3, wherein the longitudinal axes of the tapered sections 169 are substantially vertically disposed. It will also be noted that when-in its inoperative position, the longitudinal axis of the tapered section 169 of each finger 166, 167,lies

substantially in the vertical plane containing the longitudinal axis of the rack 82 or 87 to which it is pivotally attached. As the fingers 166 and 167 are being moved downwardly when the racks 82 and 87 move from the positions shown in FIG. 4 to the positions shown in FIG. 4A, the inwardly facing edge 171 of each finger section. 168 is engaged by a respective cam follower or roller 118 causing the finger with which it is associated to pivot or rock to an operative position. When in their operative positions, the inner curved faces 172 of the lips 170 contact the cylindrical body 31 of the section 30. Thus, at the commencement of'the container section stripping step of operational cycle following the container section heating step, the fingers 166 and 167 are in their operative positions since the racks 82 and 87, to which they are respectively attached, will have been previously lowered to a point where the cam followers or rollers 118 are out of engagement' with and are above the inclined cam surfaces 120 of the rack lower end portions 119. Thereafter, while the heater shells 150, 151 are being moved to their disengaged positions at the conclusion of the container heating step, the main drive gear segment'54 which was out of engagement with the pinion gear 57 during the container section heating step but which was continually rotating in a counterclockwise direction in unison with the cam 163 and gear segment 53, reengages the pinion gear 57.

As the main drive gear segment 54 thereafter continues to rotate in a counterclockwise direction the racks 82 and 87 are caused to move further downwardly from the positions assumed thereby during the container section heating step. Such further downward movement of the racks 82 and 87 causes the fingers 166 and 167 respectively carried thereby to also move downwardly therewith. It will be appreciated that as the racks 82, 87 and fingers 166, 167 continue to move downwardly after the fingers 166, 167 have assumed their operative positions, the lips 170 will engage the flange 34 of the lowermost container section 30 at diametrically opposite sides thereof, as shown in FIG. 4A, and will strip off the lowermost section 30 of the packing container 29 and thus expose a solid, generally cylindrically shaped mass of ice cream, indicated by reference character 173, which was previously enveloped by the stripped section 30, as shown in FIG. 4B.

The exposed icecream mass 173 is severed from the lower end of the packing container 29 by unique product-severing means which will not be described in detail. The'productsevering means includes a horizontally extending actuating pin 174 which is rigidly fastened to the main drive. gear segment 54. The pin 174 projects horizontally from the main drive gear segment 54 in a direction toward the cam 163 and is radially spaced between the teeth of the main drive gear segment 54 and the cam surface 162 of the cam 163. The product-severing means also includes an actuating arm 175 which has one end keyed or otherwise fixed to one end of a horizontally extending shaft 176 suitably journaled in the frame49; as shown in FIG. 2. A pinion gear 177 is also keyed to the' shaft 176 which, in turn, is in meshing engagement with a pinion gear 178 keyed to a shaft 179 also rotatably mounted in the frame 49. The product-severing means further includes a pair of severing arms 180 and 181. Each severing arm 180, 181' is generally L-shaped when in front elevation. The free end of the uppermost leg 182 ofthe arm 180 is keyed to the shaft 176 and, similarly, the free end 183 of the arm 181 is rigidly connected to the shaft I79. The lower leg portions 184 and 185, respectively, of the arms 180 and 181 are substantially U- shaped in configuration. The free ends of the lower leg portion 184 carry a tautly stretched, horizontally extending severing wire 186 therebetween. A second severing wire 187 is supported by the free ends of the lower leg portion 185 in a like fashion. The longitudinal axes of the severing wires 186 and 187 are spaced and substantially parallel to the longitudinal axes of the shafts I76 and 179. Biasing means, in the form ofa helically wound tension spring l88-operatively connected to the lower leg portion 184 of the severing arm 180 and the bracket 157, is utilized to yieldably urge the severing arms 180, 181 to their inoperative positions which positions are illustrated in FIGS. 2 and 3. When the severing arms 180, 181 are in their inoperative positions, the actuating arm extends substantially horizontal from the shaft 176. The actuating arm 175 is provided with a pivotally mounted foot 189 which, in effect, constitutes an extension thereof. The foot 189 is capable of pivoting in a clockwise direction as viewed in FIG. 2, with respect to the actuating arm 175 from its normal extended relation with the actuating arm 175 but is designed so as to be incapable of pivoting with respect to the actuating arm 175 in a counterclockwise direction. A spring 190 is employed for resiliently urging the foot 189 to its normal extended relation with the actuating arm 175. It is also to be understood that the foot 189, when in its normal extended relation with the actuating arm 175 is disposed in the arcuate path taken by the actuating pin 174 during rotation of the main drive gear segment 54. Thus, it is believed obvious that rotation of the main drive gear segment 54 in a clockwise direction, as viewed in FIG. 2, will cause the actuating pin 174 to engage the foot 189 and since the foot 189 is incapable of pivoting with respect to the actuating arm 175 when'a force is directed thereto from that side, the actuating arm 175 is caused to rock in a counterclockwise direction. Counterclockwise rocking of the actuating arm 175, in turn, effects simultaneous swinging of the severing arms and 181 and the severing wires 186, 187, respectively, carried thereby inwardly. It will be noted from viewing FIG. 4C that at the conclusion of the product-severing step, the severing wires 186 and 187 will have each travelled and cut throughthe exposed mass 173 of ice cream a distance slightly greater than the radius of the mass 173. Once the pin 174 moves out of engagement with the foot 189 during clockwise rotation of the main drive gear segment 54, the spring is effective to immediately swing the severing arms 180 and 181 to their inoperative positions. It will also be appreciated that engagement of the foot 189 by the actuating pin 174 when the main drive gear segment 54 is rotated in a counterclockwise direction, as viewed in FIG. 2, has no'effect on the severing arms 180, 181 as far as swinging themis concerned because of the one-way drive connection provided between the actuating arm 17S and the foot 189.

Preferably, the severed mass 173 is permitted to freely fall into a cup or cone or other receptacle such as a waffle-type ice cream cone 191 which is positioned on one end of a support arm 192, as shown in FIG. 2. An end section 193 of the sup port arm 192 is provided with a circular opening 194 for receiving an ice cream cone or other product receiving receptacle 191. The opposite end section 195 which is vertically offset from the end section 193, is fixedly connected to a vertical stub shaft 196 mounted for rotation in a depending bracket 197, which in turn, is rigidly attached to the bracket 146. Keyed or otherwise suitably secured to the stub shaft 196 is a bevel pinion gear 198. The support arm 192 is swung between an ice cream mass receiving station wherein an ice cream cone 191 positioned in the opening 194 is substantially in vertical alignment with the chute 43 and a delivery station removed from the ejection apparatus 42 where an ice cream filled cone 191 may be readily and conveniently removed from the support arm 192 or an unfilled cone 191 may be positioned on the support arm 192 for processing. Power for swinging the support arm between its delivery and receiving stations is obtained from a reversible single phase, AC electric delivery drive motor 199, as shown in FIG. 8. The motor shaft 200 has a bevel gear segment 20l keyed thereto which is intermittently meshahle with the bevel pinion gear 198 during rotation thereof. Rigidly fixed to the bevel gear segment 201 so as to rotate therewith is a generally L-shaped switch actuating pin 202. The pin 202 is engageable with the operating lever 203 of a motor reversing toggle switch 204 as well as the operating lever 205 of a delivery drive motor switch 206 to thereby control the direction of rotation of the delivery drive motor 199 and energization thereof. The manner in which the switches 204 and 206 function to' control the operation of the delivery drive motor 199 and thus the operation of the ice cream cone support arm 192 will be described in detail hereinafter.

OPERATION Initially, the reservoir or storage housing 12 is charged or loaded with one or more packing containers 29, each of which is filled with a solid or semisolid food product such as ice cream or the like. Each packing container 29 is positioned within the storage housing 12 so that the center portion 37 ofa respective pusher bar 36 extends vertically through the vertically aligned notches 35 formed in the flanges 34 of the packing sections 30 comprising the packing container. As pointed out herebefore, container sections 30 of a packing container 29 are intentionally oriented during assembly and processing so as to vertically align the flange notches 35. Preferably the lowermost container section 30 of each vertical packing container 29 is provided with a removable bottom cap 207 which is adapted to slidingly engage the floor 28 of the storage housing 12 prior to being positioned in the chute 43. The cap includes a radially extending flange 208 which is provided with a notch 209. The flange 208 and notch 209 are substantially the same siie as a section flange 34 and a flange notch 35 respectively. The notch 209 of the bottom cap 207 is also positioned in verticalalignment with the notches 35 of the packing container 29 with which it is associated. Assuming for the purpose of illustration that the product contents of the last container section 30 of a packing container 29 positioned in the chute 43 has been dispensed and it is desired to position a new packing container29. in the chute 43, the operator merely grasps the operating handle (not shown) and manually rotates the shaft 24 in the proper direction to cause the drum 19 and the arms 39 and the pusher bars 36 carried thereby to move in a counterclockwise direction, as viewed in FIG. 6. As pointed out herebefore, one revolution of the shaft 24 effects movement of all of the packing containers 29 disposed within the storage housing 12 simultaneously one station or step counterclockwise as viewed in FIG. 6. Thus, it will be appreciated that the particular packing container 29 that was one station removed from the chute 43 prior to rotation of the shaft 24 by the operation will now be positioned within the chute 43 and capable of being operated on by the ejection apparatus 42. It should be again reiterated that while manual means have been shown and described for indexing the drum 19 and feeding the packing container 29 to the chute 43, power means in the form of an electric motor could be adapted to and incorporated into the drum indexing structure for rotating the shaft 24 one revolution in a particular direction whenever it was desired to position a new packing container 29 in the chute 43 without departing from the spirit and scope of the invention.

At the commencement of dispensing cycle of operation, the racks 82 and 87 are intheir fully raised or uppermost positions, as shown in FIG. 3. The entire packing container 29 disposed in the chute is supported by the dogs 99 which are also in their uppermost positions. The lips 100 of the dogs 99 are in engagement with the flange 34 of the second container section 30 from the bottom of the packing container 29. When the racks 82 and 87 arein their fully raised positions, the sliding stop members 107 are in their retracted positions and the pawls 128 respectively associated therewith are, obviously, in their uncooked conditions, as described hereinbefore, The severing arms 180 and 181 are in their inoperative positions and the heater shells 150 and 151 are fully retracted, as shown in FIG. 3. The actuating pin 174 rigidly fixed to the main drive segment 54 is in engagement with the end of an operating lever 210 ofa delivery drive motor starting switch 211 which, in turn is in engagement with the end of an operating lever 212 of the main drive motor switch 90, as illustrated in FIG. 8, When the actuating pin 174 is in the position shown in FIG. 8, the operating lever 212 is depressed and the switch contacts (not shown) of the main drive motor switch are open while the operating lever 210 of the delivery drive-motor starting switch 211 is not depressed although the switch contacts (not shown) thereof are also open. The operating lever 230 of the reversing toggle switch 89 for controlling the direction of rotation of the shaft ofthe main drive motor 88 and, thus, the main drive shaft 52, is in its right-hand position as illustrated in FIG. 8. Energization of the main drive motor 88 with the operating lever 231 in such right-hand position effects counterclockwise rotation of the main drive shaft 52, as viewed in FIGS. 2 and 8.

The electrical circuit for supplying the main drive motor 88 and the delivery drive motor 199 with electric current includes a pair of conductors 213, 214 suitably connected to a source of electrical energy. One terminal of the main drive motor starter switch 91 is connected to the conductor 213. The starter switch 91 is preferably a simple single-pole, singlethrow, pushbutton type wherein the two contacts of the switch are spring-pressed out of engagement and the contacts are 4 closed by depression of the pushbutton. The other contact of the starter switch 91 is connected to a conductor 215. The conductor 213 is electrically connected to one terminal 216 of the delivery drive motor switch 211, one terminal 217 of the main drive motor switch 90 and one terminal 218 of the delivery drive motor switch 206. The conductor 215 is electrically connected to a terminal 219 of the reversing toggle switch 89 and to the main drive motor 88. The conductor 215 is also electrically connected to a terminal 220 to the main drive motor switch 90. Conductor 214 is electrically connected to a terminal 221 of the reversing toggle switch 89 and the main drive motor 88. In a similar fashion, the delivery drive motor 199 and one terminal 222 of the reversing toggle switch 204 are also electrically connected to the conductor 214. A conductor 223, having one end connected to terminal 224 of the delivery drive motor switch 211, leads to a terminal 225 of the delivery drive motor switch, a terminal 226 of the reversing toggle switch 204, and the delivery drive motor 199. In addition to the foregoing, the electric control circuit for the operation of the motors 88 and 199 includes conductor means electrically interconnecting the motor 88 with a common terminal 227 of the reversing toggle switch 89 and the motor 199 with the common terminal 228 of the reversing toggle switch 204.

At the commencement of an operational or dispensing cycle and prior to energization of the electric control circuit means, the ice cream cone or product-receiving receptacle supporting arm 192 disposed at its delivery station, as defined hereinbefore. When the supporting arm 192 is disposed at its delivery station, the actuating pin 202 carried by the bevel gear segment 201 is in engagement with and is depressing the operating lever 205 of the delivery drive motor switch 206. The operating lever 203 of the delivery drive motor reversing toggle switch 204 is in its left-hand position, as viewed in FIG. 8. It is to be understood, that when the operating lever 205 is depressed, the contacts of the switch 206 are open and when the operating lever 203 is in its left-hand position, the motor 199 is conditioned so that the shaft 200 thereofwill rotate in a clockwise direction, as viewed in FIG. 8, if energized. Movement of the actuating pin 202 away from the switch operating lever 205 as the bevel gear segment 201, which is coupled to the motor shaft 200, is rotated in a clockwise direction, as viewed in FIG. 8, permits resilient means (not shown) incorporated into the switch 206 to close the contacts thereof so as to complete the electrical circuit through the switch 206.

With the various components of the ejection apparatus 42 oriented as pointed out above and the electrical control circuit including the reversing toggle switch 89, main drive motor switch 90, starter switch 91, reversing toggle switch 204, delivery drive motor switch 206, and delivery drive motor starter switch 211 conditioned as described above, the operator first places a w.affletype cone 191 or the like in the opening 194 of the support arm 192, which is at its delivery station remote from the ejector apparatus 42. Thereafter, the operator merely depresses the pushbutton of the main drive motor starter switch 91 so as to complete an electrical circuit between the main drive motor 88 and the source of electric energy. It is to be understood that means other than the pushbutton main motor starter switch 91 could be employed for initially energizing the electric motor 88 and starting the dispensing cycle without departing from the spirit and scope of the invention. As an example, a coin operated switch of a well-known type wherein the deposit of a coin in a slot or the like is effective to cause closing of the switch contacts could be used in lieu of the manually operated started switch 91 if desired. Immediately upon energization of the main drive motor 88, the main drive gear segment 54 will commence to rotate in a counterclockwise direction, as viewed in FIGS. 2 and 8. Once the main drive gear segment 54 has rotated a relatively small amount, the actuating pin 174 moves sufficiently away from the switch operating lever 212 so as to no longer depress the same. When this occurs, as stated hereinbefore, the contacts of the main drive motor switch 90 close to thus complete an energizing electrical circuit to the main drive motor 88 independently of the condition of the starter switch 91, and, hence, it is no longer necessary for the operator to continue depressing the starter switch 91 pushbutton in order to maintain the main drive motor 88 in operation. Counterclockwise rotation of the main drive gear segment 54 from the position illustrated in FIG. 2, which position corresponds to the at rest or start condition of the ejection apparatus 42, will effect clockwise rotation of the pinion gears 57 and 58 and, through the intermediary of idler gears 83 and 84, simultaneous counterclockwise rotation of pinion gears 63 and 64.

counterclockwise rotation of the main drive gear segment 54 also causes the bevel gear segment 55, which is keyed to the main drive shaft 52, to rotate counterclockwise and such counterclockwise rotation of the bevel gear segment 55 is effective to rotate the bevel pinion gear 76 in a counterclockwise direction. Such counterclockwise rotation of the bevel pinion gear 76'and the shaft 74 to which it is keyed, causes the flaps 77, 79 to swing simultaneously from their horizontal, chute-closing positions, as shown in FIG. 3, to their generally vertical, fully open positions, illustrated in FIG. 4.

As pointed out hereinbefore, concurrent clockwise rotation of the pinion gear 58 and counterclockwise rotation of the pinion gear 64 will commence moving the racks 82 and 87, respectively, and the packing container 29 disposed within the chute 43 and supported on the lips 100 of the rack-supported dogs 99 vertically downwardly. The racks 82 and 87 continue to move downwardly and shortly before the main drive gear segment 54, which is still rotating in a counterclockwise direction, disengages from the pinion gear 57, the racks 82 and 87 will have moved downwardly to positions where the shoulders 104 of the dogs 99 are moved out of abutting engagement with the flat edge surfaces 96 of the plates 59 and 60 of the gear and rack housings 61 and 67, which dog positions are partially illustrated in FIG. 4. Obviously, when the dogs 99 are permitted to pivot to such positions, the entire packing container 29 disposed within the chute 43 is released and allowed to drop freely until the flange 34 of the second container section 30 from the bottom of the packing container 29 or the flange 34 of the lowermost container section 30 if the bottom cap 207 is still in place and. has not already been removed by the ejection apparatus 42 is caught by the stop members 107 and the pawls 128.

The stop members 107 are moved from their retracted position, illustrated in FIG. 3, toward their fully extended positions, shown in FIG. 4A, so as to be in the proper position to engage or catch the section flange 30 in the aforesaid manner by the camming action afforded by the wedge-shaped end portions 119 of the racks 82 and 87 moving downwardly with respect to the cam followers or rollers 118. It will also be uppreciated that the pawl 128 which were in their uncocked conditions at the start of the operational cycle, as also moved inwardly with the stop members 107 so as to position the flat surfaces 132 of the pawl legs 133 in the path of the flange 34 of the lowermost container section 30 at the moment the packing container 29 is released from the dogs 99 as shown in FIG. 4. Thus, as the packing container 29 freely falls in the chute 43, the flange 34 of such lowermost container section 30 first engages the pawls 128 and flips them to the cocked conditions, as illustrated in FIG. 4A. As pointed out hereinbefore, when the pawls 128 are in their cocked conditions and the stop members 107 are in'their fully extended positions or are approaching such fully extended positions, the uppermost surfaces 139 of the stop members-107 and the flat surfaces 134 adjacent the pawl tips 138 are in position to engage the section flange 30 of the second container section 30 from the bottom so as to prevent further descent of the packing container 29, as clearly shown in FIG. 4A.

The racks 82 and 87 become stationary in the positions illustrated in FIG. 4A upon disengagement of the main drive gear segment 54 from the pinion gear 57 although the main drive gear segment 54 continues to rotate in a counterclockwise direction. During rotation of the main drive gear segment 54 to effect movement of the racks 82 and 87 from the positions shown in FIG. 4 to the positions illustrated in FIG. 4A, the stripping fingers 166, 167 are moved from their inoperative positions to their operative positions wherein the enlarged, arcuately shaped lips 170 are in engagement with the section flange 34 of the lowermost container section 30.

Simultaneously with the aforesaid counterclockwise rotation of the main drive gear segment 54 to effect movement of the racks 82 and 87 from the positions shown in FIG. .4 to the position shown in FIG. 4A, the gear segment 53 will rotate counterclockwise and drive the rack 140 downwardly and such downward movement of the rack 140 will cause the heater shells and 151 to move from their disengaged positions to positions wherein they firmly embrace the body 31 of the lowermost container section 30. As pointed out hereinbefore, the heater shells 150 and 151 are maintained in embracing relationship with the cylindrical body 31 of the lowermost container section 30 by the latch means 154 even though the gear segment 53 is moved out of meshing engagement with the rack 140. Electrical current is supplied to the heater shells 150, 151 while they are in their container section-engaging positions, as illustrated in FIG. 4A, so as to melt or soften the ice cream or other material within and adjacent the cylindrical body 31 and facilitate stripping of the container section 30 from the ice cream mass 173. The heater shells 150, 151 are, in effect, locked in their container section-engaging positions until the leading edge of the cam 163, which continues to rotate in a counterclockwise direction, as viewed in FIG. 1, in unison with the main drive gear segment 54, operatively engages the latch plunger 156 to move the same out of locking engagement with the rack 140. At the moment this occurs, the springs 152 and 153 are effective to return the heater shells 150, 151 immediately to their fully disengaged positions.

As the main drive gear segment 54continues to rotate in a counterclockwise direction, it moves into reengagement with the pinion gear 57, which as indicated before, controls raising and lowering of the racks 82 and 87. Immediately upon reengagement of the main drive gear segment 54 and the pinion gear 57, the racks 82 and 87 commence to move further downwardly from the positions occupied thereby during the above-described heating step and since the enlarged, arcuately shaped lips of the fingers 166, 167 have already been moved in operative engagement with the flange 34 of the lowermost container section 30, such further downward movement will strip off the heated lowermost section 30 of the packing container 29, as illustrated in FIG. 4B, and thus expose the ice cream mass 173 to be dispensed by the dispenser 10 during the operational cycle being described. Preferably, the stripped container section 30 falls into an opening (not shown) vertically aligned with and below the-chute 43, of a bin (not shown) or the like.

step, are established whenthe main drive gear segment 54 ceases to rotate in a counterclockwise direction, as viewed in FIG. 1, and begins .to rotate in a clockwise direction. Obviously, reversal of the direction of rotation of the main drive gear segment 54 requires reversal of the direction of rotation of the main drive motor 88. Reversal of the direction of rotation of the main drive motor 88 is accomplished by an actuating arms 229 of a trip element 230 which is moved into operative engagement with the operating lever 231 during continued counterclockwise rotation of the main drive gear segment 54 following reengagement of the pinion gear 57 therewith. The arm '229 of the trip element 230, which is mounted on one side of the. main drive gear segment 54 for limited relative pivotal or rocking movement, is engageable with the reversing toggle switch operating lever 231, which is in its right-hand position, asviewed in FIG. 8, during the entire operational cycle up to this time, to force the same overcenter and to its left-hand position and cause the direction of rotation of the motor 88 to immediately reverse. It will be appreciated that reversal of the direction of rotation of the motor 88 simultaneously results in the main drive gear segment 54 being rotated in a clockwise direction.

As evidenced by viewing FIG. 8B, trip element 230 includes, in addition to actuating arm 229, a pair of radially extending arms 232, and 233. The arms 232 and 233 are angularly spaced with respect-to each other and the actuating arm 229. An axially extending stop pin 234 is fixed to the main drive gear segment 54 and is adapted to be engaged by a flat surface 235 of the arm 232 to limit counterclockwise rotation of the trip element 230 relative to the main drive gear segment 54 and by a flat surface 236 of the arm 233 to limit counterclockwise rotation of the trip element 230 relative to the main drive gear segment 54, as'viewed in FIG. 8A. It will be appreciated from the foregoing that during the latter part of the aforementioned counterclockwise rotational movement of the main drive gear segment 54 following reengagement therewith of the pinion gear 57, the actuating arm 229 of the trip element 230 will first engage the main drive motor reversing switch operating lever 231, which is in its right-hand position as viewed in FIG. 8, and be rotated clockwise with respect to the main drive gear segment 54 until the flat surface 236 ofthe trip element arm 233 engages the stop pin 234. Thereafter, continued counterclockwise rotation of the main drive gear segment 54 will cause the operating lever 231 of the main drive motor reversing switch 89 to snap or flip over to its lefthand position resulting in reversal of the direction of rotation of the main drive gear segment 54.

Inasmuch as the main drive gear segment 54 is in meshing engagement with thepini'on gear 67 at the commencement of the rotation direction reversal, such clockwise rotation of the main drive gear segment 54 immediately causes the racks 82 and 87 to start elevating The racks 82 and 87 continue to elevate until the main drive gear segment 54 disengages from the pinion gear 57 at' which point in the operating cycle further upward movement of the racks 82 and 87 ceases momentarily. It will be appreciated that during such initial clockwise movement of the main drive gear segment 54, the fingers 167 and 168 are raised in unison with the racks 82 and 87, respectively. However, they are still in their operative positions when further upward movement of the racks 82, 87 momentarily ceases since the racks 82,.87 will not have been elevated sufficiently to permit the fingers 167, 168 to swing or return to their inoperative positions. Nevertheless, the stripping fingers 167, 168 will have been elevated sufficiently so as to not be in the path of movement of the severing wires 186 and 187 or be in positions that would hamper the operation of the product-severing means which immediately follows the above-described stripping step.

As the main drive gear segment 54 continues to rotate in a clockwise direction and after the stripping finger I66 and 167 have been elevated to the raised positions shown in FIG. 4C the actuating pin 174 carried by the main drive gear segment 54 engages the foot 189 of the actuating arm and effects counterclockwise rocking of the actuating arm 175, as viewed in FIG. 2. As pointed out herebefore, such counterclockwise rocking of the actuating arm 175 causes severing arms and 181 to simultaneously swing from their inoperative positions to their product-severing positions, illustrated in FIG. 4C, against the resilient action of the spring 188. It will be appreciated that when the severing arms 180 and 187 are effective to cleanly and efficiently cut through the exposed ice cream mass 173 adjacent the bottom edge of the cylindrical body 31 of the lowermost container section 30. The severed ice cream mass 173 freely falls and is received in the ice cream cone 191 previously positioned on the support arm 192. The manner in which the support arm 192 is moved from its delivery station, where it was located prior to this point in the operational cycle, to its receiving station will be pointed out presently. Once the actuating pin 174 moves out of engagement with the foot 189 as the main drive gear segment 54 continues to rotate clockwise, the spring 188 is effective to rapidly return the severing arms 180 and 181 to their retracted, inoperative positions.

As the main drive gear segment 54 continues to rotate in a clockwise direction following disengagement of the actuating pin 174 with the foot 189, it eventually remeshes with the pinion gear 57 causing the racks 82 and 87 to once again start moving upwardly from the stationary positions occupied thereby during the product-severing step described above. The racks 82 and 87 continue to move upwardly until they reach the positions assumed thereby at the end of the operational cycle which positions are illustrated in FIG. 2. It will be observed from viewing FIGS. 4C and 2 in sequential order that during such incremental upward movement of the racks 82 and 87, the shoulders 104 of the dogs 99 are brought into sliding engagement with the flat vertical edge surfaces 96 of the plates 59, 60, 65, and 66 causing the dogs 99 to pivot in unison to positions wherein the lips 100 of the dogs 99 engage the underside of the section flange 34 of the second container section 30 from the bottom of the packing container 29 at diametrically opposite points thereof. Thereafter, further raising of the racks 82 and 87 effects concurrent elevation of the entire packing container 29 into the refrigerated storage housing 12. It will be appreciated that during such further raising of the racks 82 and 87, the stripping fingers 166 and 167 will have been elevated sufficiently to permit them to swing or return to their inoperative positions and out of engagement with the packing container 29.

As the racks 82 and 87 are being elevated and are approaching their uppermost positions, illustrated in FIG. 2, the trip element actuating arm 229 comes into abutting engagement with the main drive gear segment 54 continues to rotate clockwise thereafter, the trip element 230 is rocked in a counterclockwise direction with respect thereto until the flat surface 236 of the arm 233 engages the stop pin 234. There after a smooth increment of angular movement of the main drive gear segment 54 simultaneously effects movement of the reversing switch operating lever 231 from its left-hand position to its right-hand position, as illustrated in FIG. 8, through the intermediary of the trip element 230, and actuation of the delivery drive motor starting switch operating lever 210 and the main drive motor switch operating lever 212 in unison by the actuating pin 174. As pointed out herebefore, when the actuating pin. 174 is oriented and in operative engagement with the switch operating levers 210 and 212 as illustrated in FIG. 8, the contacts of both the delivery drive motor starting switch 211 and the main drive motor switch 90 are both open. Hence, when this occurs power to both the main drive motor 88 and the delivery drive motor 199 is disrupted and vertical upward movement ofthe racks 82 and 87 ceases.

As the packing container 29 is being elevated into the refrigerated housing 12 by clockwise rotation of the main drive gear segment 54, the bevel gear segment 55, which is keyed to the main drive shaft 52, also rotates clockwise and is adapted to move into meshing engagement with the bevel pinion gear 76. When this occurs, continued clockwise rotation of the bevel gear segment 55 thereafter causes the flaps 77 and 79 to simultaneously swing from their open positions toward their generally horizontally disposed, closed positions. It is to be understood that the flaps 77 and 79 are in their closed positions by the time power to the main drive motor 88 is disrupted at theend of the operational cycle.

The operation of the means for delivering an empty ice cream cone 191 to the-chute 43 for receiving the severed ice cream mass 173 and delivering the filled ice cream cone to a delivery station will now be described in detail. As pointed out herebefore, at the start of the operation cycle, the support arm 192 is at its delivery station, and the contacts of the delivery drive motor starting switch 211 are open. The L-shaped switch actuating pin 202 carried by the bevel gear segment 201 is in engagement with and depressing the operating lever 205 of the delivery drive motor switch 206. The contacts of the delivery drive motor switch 206 are open when the operating lever 205 is depressed, as shown in FIG. 8.'Also, the operating lever 203 of the delivery drive motor reversing switch 204 is conditioned to cause the delivery drive motor shaft 200 to rotate in a clockwise direction when the motor 199 is energized. The contacts of the delivery drive motor starting switch 21] remain open-during the entire operational cycle except when the operating lever 210 is depressed momentarily by the actuating pin 174 at the moment the main drive gear segment 54 changes its direction of rotation from counterclockwise to clockwise. Immediately following depression of the operating lever 210 as shown in FIG. 8A the delivery drive motor 199 will be energized and the delivery drive motor shaft 200 and the bevel gear segment 201 keyed thereto will commence rotating in a clockwise direction. Rotation of the bevel gear segment 201 in a clockwise direction will simultaneously cause the actuating pin'202 to move out of depressing engagement with the operating lever 205 of the delivery drive motor switch 206 and the support arm 192 to commence swinging from its delivei'y station to its receiving station. Thus, even though the actuating pin 174 will have moved out of depressing engagement with the operating lever 210, the circuit of energizing the delivery drive motor 199 will remain completed by virtue of the closed condition of the delivery drive motor switch 206 independently of the condition of the delivery drive-motor starting switch 211. As the bevel gear segment 201 continues to rotate in a clockwise direction as viewed in FIG; 8, it disengages from the bevel gear 198. When disengagement of the bevel gear segment 201 from the bevel gear 198 occurs, the support arm 192 will have been swung to its receiving station and its remains in such receiving station until the bevel gear segment 201 reengages the bevel gear 198 during subsequent counterclockwise rotation of the bevel gear segment 201. As the bevel gear segment 201 continues rotating in a clockwisedirection following disengagement of the bevel gear 198, the actuating pin 202 eventually moves into engagement with the operating lever 203 (which is in its lefthand position, aspointed out hereinbefore) of the delivery drive motor reversing switch 204 and flips the same to itsright hand position. When this occurs, the direction of rotation of the delivery drive motor 199 is immediately reversed and, consequently, the bevel gear segment 201 commences to rotate in a counterclockwise direction. The bevel gear segment 201 reengages the bevel gear 198 during such counterclockwise rotation to thereby effect swinging of the support arm 192 from its receiving station, where the ice cream cone 191 received the mass of ice cream 173 which was severed from the packing container 29 during the severing step described above, to the delivery station. At the moment the support arm 192 reaches its delivery station, the actuating pin 202 will have simultaneously forced the delivery drive motor reversing switch operating lever to its left-hand position or the position assumed thereby at the start of the operational cycle and depressed the operating lever 205 of the delivery drive motor switch 206 to thereby disrupt energization of the delivery drive motor 199. It will be appreciated that the dispenser 10 is now conditioned for the start of another dispensing cycle ofoperation.

Iclaim:

1. A dispenser mechanism for dispensing material of semisolid consistency contained in a multisectional packing c'ontainer comprising: first support means operatively engageable with a packing container for supporting the same with the longitudinal axis thereofextending vertically; means for removing the container section from one end of said packing container and from the mass of material contained therein while said packing container is in operative engagement with said support means; and means for severing said mass of material from said packing container following removal of said container section thereof.

. 2. A dispenser mechanism as set forth in claim 1, wherein said means for removing the container section from one end of said packing container and from the mass of material contained therein includes stripping means actuatable into and out of operative engagement with said container section; and means for moving said container section and said stripping means, when in operative engagement with said container section, relatively to the other end of said packing container a predetermined distance substantially along the longitudinal axis of the packing container to effect removal of said container section from the packing container and from the mass of material contained in said removed container section.

3. A dispenser mechanism as set forth in claim 2, wherein said means for removing the container section from one end of said packing container and from the mass of material contained therein further includes means for heating said container section to reduce adherence of the material to said container section and thereby facilitate removal of said container section from said mass ofmaterial contained therein.

4. A dispenser mechanism as set forth in claim 1, including a storage housing means capable of enclosing a plurality of packing containers therewithin; and means for moving one of said containers between a first position wherein it is disposed entirely within said storage housing means and a second position wherein it is in operative engagement with said first support means.

5. A dispenser mechanism as set forth in claim 4, wherein said storage housing means includes floor means for supporting packing containers with their longitudinal axes extending vertically, said floor means having an opening therethrough for the passage ofa packing container vertically therethrough, said first support means being vertically spaced below said opening; and wherein said means for moving one of said packing containers between said first and second positions includes second support means operatively engageable with a packing container, said second support means being vertically movable between a first elevated position wherein said packing container is disposed and supported within said storage housing and a second, lowered position wherein at least a portion of said packing container is disposed below said opening, said second support means being responsive to movement vertically downwardly beyond said second, lowered position to operatively disengage said packing container and permit said packing container to move into operative engagement with said first support means.

6. A dispenser mechanism as set forth in claim 5, wherein said floor means is substantially annular in shape in vertical plan and said opening is at the bottom of a feed chute, said feed chute being radially offset from said annular floor means and being partially defined by a generally semicylindrical wall portion of said storage housing means, said feed chute being effective to guide a packing container disposed therein during vertical movement thereof with respect to said storage housing means; and means for moving a packing container supported on said floor means and positioning the same in said feed chute and in operative engagement with said second support means.

7. A dispenser mechanism as set forth in claim 6, wherein said storage housing means includes a generally cylindrical 

